EP4019397B1 - Aktuatorüberdruckanordnung - Google Patents

Aktuatorüberdruckanordnung Download PDF

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Publication number
EP4019397B1
EP4019397B1 EP20306656.8A EP20306656A EP4019397B1 EP 4019397 B1 EP4019397 B1 EP 4019397B1 EP 20306656 A EP20306656 A EP 20306656A EP 4019397 B1 EP4019397 B1 EP 4019397B1
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EP
European Patent Office
Prior art keywords
mode
pressure
assembly
actuator
valve
Prior art date
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Active
Application number
EP20306656.8A
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English (en)
French (fr)
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EP4019397A1 (de
Inventor
Karl POTIER
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Goodrich Actuation Systems SAS
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Goodrich Actuation Systems SAS
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Goodrich Actuation Systems SAS filed Critical Goodrich Actuation Systems SAS
Priority to EP20306656.8A priority Critical patent/EP4019397B1/de
Priority to CA3140331A priority patent/CA3140331A1/en
Priority to US17/541,410 priority patent/US11821443B2/en
Priority to BR102021025631-1A priority patent/BR102021025631A2/pt
Publication of EP4019397A1 publication Critical patent/EP4019397A1/de
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/028—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force
    • F15B11/032—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force by means of fluid-pressure converters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/028—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force
    • F15B11/032—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force by means of fluid-pressure converters
    • F15B11/0325—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force by means of fluid-pressure converters the fluid-pressure converter increasing the working force after an approach stroke
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B3/00—Intensifiers or fluid-pressure converters, e.g. pressure exchangers; Conveying pressure from one fluid system to another, without contact between the fluids
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B64—AIRCRAFT; AVIATION; COSMONAUTICS
    • B64C—AEROPLANES; HELICOPTERS
    • B64C13/00—Control systems or transmitting systems for actuating flying-control surfaces, lift-increasing flaps, air brakes, or spoilers
    • B64C13/24—Transmitting means
    • B64C13/38—Transmitting means with power amplification
    • B64C13/40—Transmitting means with power amplification using fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
    • F15B2211/214—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being hydrotransformers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/52—Pressure control characterised by the type of actuation
    • F15B2211/526—Pressure control characterised by the type of actuation electrically or electronically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/52—Pressure control characterised by the type of actuation
    • F15B2211/528—Pressure control characterised by the type of actuation actuated by fluid pressure

Definitions

  • the present invention relates to the field of hydraulic actuators such as, but not exclusively, actuators used in aircraft.
  • Actuators are used in many applications where a load such as a component or surface is to be moved. Many fields utilise hydraulic actuators that operate due to pressure differences to cause movement of an actuator rod or piston that causes corresponding movement of the load.
  • Actuator assemblies are disclosed in WO2011/064344 and DE 10 2012 003181 .
  • an actuator pressure intensifying assembly as defined by claim 1.
  • the gear motor assembly preferably comprises a gear motor and a gear pump connected via a torque shaft, the gear motor and the gear pump arranged such that in the second mode, the supply pressure flows through the mode valve to the gear motor to cause the motor to rotate, and wherein torque from rotation of the motor is transmitted to the gear pump to provide increased pressure that is returned to the mode valve and provided to the actuator.
  • the valve is arranged to change from the first mode to the second mode in response to the supply pressure exceeding the predetermined threshold pressure e.g. 17236.9 kPa (2500 psi).
  • an actuator assembly comprising an electrohydraulic servovalve (EHSV) to provide the supply pressure, and an actuator to receive the control pressure and an actuator pressure intensifying assembly as defined above between the EHSV and the actuator.
  • EHSV electrohydraulic servovalve
  • An EHSV mode valve may be provided between the EHSV and the mode valve.
  • the actuator is for moving an aircraft part such as a flap.
  • the solution provided by the present invention is to locally increase the supply pressure to the actuator when required using a compact assembly of a mode select valve and a motor pump assembly.
  • the actuator 1 comprises a housing or cylinder 10 within which is mounted an axially moveable rod or piston 11 having a piston head 12 extending across the interior 13 of the housing 10.
  • the piston head 12 separates the interior of the housing into an extension chamber 14 on one side of the head and a retraction chamber 15 on the other side of the head.
  • the end 16 of the piston 11 furthest from the head extends from the housing and is arranged to be coupled to the load (not shown) to be moved.
  • Pressure ports 17, 18 are provided in the housing to receive pressurised fluid to, respectively, the extension chamber 14 and the retraction chamber 15, as required to move the load.
  • the piston will either extend relative to the housing (arrow A) or retract into the housing (arrow B), causing corresponding movement of the load.
  • Pressurised fluid is provided to the actuator chambers, according to the desired direction of movement of the load, from a pressure source (not shown) through an electrohydraulic servovalve (EHSV) (not shown) and then via an EHSV mode valve 20.
  • Pressurised fluid is provided from the EHSV to the EHSV mode valve via supply ports 21,22.
  • a spool body 23 of the EHSV mode valve moves relative to the supply ports 21,22, according to a control command indicative of the desired load movement, to create flow channels from the supply ports through the EHSV (not shown) and the EHSV mode valve 20 by aligning openings in the spool body with the supply ports and control or return ports 24,25 as desired.
  • control and return ports are, conventionally, connected by fluid lines 26,27 to the extension and retraction chambers of the actuators.
  • more or less pressure will be provided to the extension chamber compared to the retraction chamber, thus causing movement of the piston and, therefore, of the load.
  • the spool body 23 will be controlled to create a flow passage from supply port 21 to control port 24, the pressurised fluid is then provided via line 26 and port 17 to the extension chamber 14 of the actuator 10.
  • the pressure in this chamber will exceed that in the retraction chamber 15, causing the piston to move in direction A.
  • ports 22, 25 and 18 are aligned to reverse the balance of pressure. This works well for relatively low pressure loads, where the supply pressure is sufficient to provide the required output from the actuator. For higher output requirements, however, the supply pressure would need to be greatly increased for the same design of actuator. As discussed above, this is not always feasible.
  • the solution provided by the present invention is to provide an assembly between the EHSV mode valve 20 and the actuator 10 that can boost the actuator input pressure for higher output requirements.
  • the assembly comprises an intermediate mode valve 30 and a gear motor assembly 40 as will be described in more detail below.
  • this assembly In the normal operating mode, for low pressures below a predetermined activation pressure, as shown in Fig. 1 , this assembly will be transparent -i.e. the actuator system will operate as if it were not there and will, therefore, operate as described above for conventional systems. Fluid from the EHSV and EHSV mode valve 20 will pass directly through passages in the intermediate mode valve 30 to the actuator. A benefit of this is that oil flow is not affected by the system, so large flow rate can be achieved and actuator maximum speed rate is not affected.
  • the spool body 23 in the normal operating mode, when the load is to be moved by the piston moving in direction A, the spool body 23 will be controlled to create a flow passage from supply port 21 to control port 24, the pressurised fluid is then provided via line 26 to a first end 31 of the intermediate mode valve 30, through a flow channel 32 and out through an outlet port 33 connected by line 34 to port 17 of the actuator and to the extension chamber 14 of the actuator 10.
  • the pressure in this chamber will, as before, exceed that in the retraction chamber 15, causing the piston to move in direction A.
  • ports 22, 25 and 18 are aligned via second end 35 of the intermediate mode valve 30, channel 36 and port 37 to reverse the balance of pressure.
  • the actuator 10 is required to provide a higher output. It may be that the supply pressure (not shown) can be increased somewhat, but not enough to achieve the output requirement using the conventional assembly described above. For example, an output of, say, over 34473.79 kPa (5000 psi) may be required but the maximum supply pressure is, say, only 20684.3 kPa (3000 psi). In such situations, the assembly of the present disclosure kicks in to boost the supply pressure to provide the required output.
  • the assembly is configured, as mentioned above, to be transparent for lower pressures and to only kick in for pressures above a predetermined activation pressure. This will be described in relation to Fig. 2 , where, in the example, the activation pressure is, say 17236.9 kPa (2500 psi).
  • the elements shown in Fig. 2 are the same as shown in Fig. 1 and the same reference numerals will be used.
  • the pressure required by the actuator 10 is 40679 kPa (5900 psi) but the maximum supply pressure is 20684.3 kPa (3000 psi) as shown in Fig. 2 .
  • the supply pressure exceeds the activation threshold e.g. exceeds the 17236.9 kPa (2500 psi) of the normal operating mode described in relation to Fig.
  • the pressure (now, in this example 20684.3 kPa (3000 psi)) from the EHSV mode valve at port 24, provided to the first end 31 of the intermediate mode valve 30 via line 26 will be sufficient to overcome the forces of the springs 38,39 at the ends of the intermediate mode valve that, in the normal operating mode, hold the valve in the position wherein the channels 32 and 36 are aligned with ports 33 and 37 so creating a direct passage through the intermediate valve.
  • the springs 38, 39 are selected such that as the pressure at the first end 31 exceeds the activation pressure, the spring 39 at the second end 35 compresses causing the spool 300 of the intermediate mode vale 30 to move towards the second end i.e., in this example, direction A.
  • the high pressure applied to the first end 31 of the intermediate mode valve 30 therefore passes through channel 32 to line 44 via output port 42, and to the gear motor assembly 40.
  • the gear motor assembly 40 acts as a local pressure intensifier for the actuator as will now be described.
  • the gear motor assembly 40 includes a gear motor 50 connected via a torque shaft 51 to a gear pump 52. Input pressure to the gear motor 50 comes from line 44 via an inlet port 53. The other side of the gear motor 50 is connected to the low pressure return line 54 of the system. The pressure differential across the gear motor 51 causes the motor to rotate and generates a torque. This torque is transmitted, via the torque shaft 51, to the gear pump 52.
  • the high pressure fluid from port 42 is also provided to an inlet port 55 of the gear pump 52. Operation of the gear pump 52 due to the transmitted torque increases the pressure of the fluid from port 55 and fluid at the increased pressure (here, as an example 40679 kPa (5900 psi)) is output at output port 56 of the gear pump 52. This increased pressure fluid flows along line 57 back to the intermediate mode valve 30 via port 41. It then passes through channel 45 and flows out of the intermediate valve 20 via port 33 through line 58 into the extension chamber 14 of the actuator 10.
  • the intensified pressure applied to the extension chamber 14 greatly exceeds that in the retraction chamber 15 resulting in a high force movement of the actuator piston in direction A, sufficient to drive the high load.
  • the overlap of the intermediate mode valve's ports is selected such that when the pressure threshold is reached, port 42 is connected to port 31 before port 33 is connected to port 41.
  • the assembly works in the opposite direction in a symmetrical and analogous manner.
  • port 31 is connected to the return port and port 35 to the high pressure port.
  • the pressure at ports 31 and 42 quickly decreases and gear pump 52 starts to turn in the opposite direction, thus pumping hydraulic fluid from the extension chamber to the return port.
  • the return line 54 should be connected to the return port of the EHSV (not shown) to avoid hydraulic fluid being pumped into aircraft return lines.
  • port 35 is still connected to port 37 so that when the direction changes from extension to retraction, the actuator can quickly start to move in the opposite direction without any time lag.
  • the sizes of the springs are selected to define the pressure threshold, and the gear motor pitch diameter are selected according to the desired maximum operating speeds and pressures.
  • the assembly only uses a single hydraulic circuit and so the risks of leakage and other hazards associated with hydraulic circuits are minimised.
  • the assembly changes between modes autonomously, without any need for manual or controlled switching and without the need for any additional power source.
  • the assembly for intensifying the pressure -i.e. the intermediate mode valve and the gear motor assembly can be configured in a compact assembly that can be positioned in locations where there is not much space e.g. on or near an aircraft wing.
  • the assembly can be fitted to the actuator mounting manifold or spaced from the manifold. The compact arrangement therefore allows some freedom in design and location of the overall system.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Automation & Control Theory (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Fluid-Pressure Circuits (AREA)

Claims (6)

  1. Aktuatorüberdruckanordnung, umfassend ein Modusventil (30) und eine Getriebemotoranordnung (40), wobei das Modusventil angeordnet ist, um an einem Eingangsanschluss (31) einen Versorgungsdruck zu empfangen und an einem Ausgangsanschluss (33) einen Steuerdruck an einen Aktuator bereitzustellen, wobei das Modusventil ferner konfiguriert ist, um sich als Reaktion darauf, dass der Versorgungsdruck einen vorbestimmten Aktivierung-Schwellenwertdruck überschreitet, von einem ersten Modus, in dem der Versorgungsdruck direkt von dem Eingangsanschluss zu dem Ausgangsanschluss in einem ersten Fluidströmungspfad strömt, und einem zweiten Modus, in dem der Versorgungsdruck von dem Eingangsanschluss zu dem Ausgangsanschluss in einem zweiten Fluidströmungspfad strömt, der die Getriebemotoranordnung zwischen dem Eingangsanschluss und dem Ausgangsanschluss beinhaltet, zu bewegen, was den Versorgungsdruck derart verstärkt, dass der Steuerdruck höher als der Versorgungsdruck ist;
    wobei das Modusventil (30) einen Ventilkörper und einen Schieber (300) umfasst, der für eine Axialbewegung innerhalb des Ventilkörpers angeordnet ist, wobei der Ventilkörper den Eingangsanschluss (31) und den Ausgangsanschluss (33) definiert und ferner Auslassanschlüsse (41, 42) für den zweiten Modus definiert, und wobei das Modusventil derart angeordnet ist, dass in dem ersten Modus der Schieber (300) angeordnet ist, um einen Strömungspfad zwischen dem Eingangsanschluss (31) und dem Ausgangsanschluss (33) bereitzustellen und die Ausgangsanschlüsse (41, 42) des zweiten Modus zu blockieren, und um in dem zweiten Modus einen Strömungspfad von dem Eingangsanschluss (31) zu einem Ausgangsanschluss (42) des zweiten Modus bereitzustellen, der mit der Getriebemotoranordnung verbunden ist; und wobei das Modusventil ferner eine Feder (38, 39) an jedem Ende des Schiebers (300) umfasst, wobei die Federn derart ausgewählt sind, dass in dem ersten Modus der Schieberkörper durch die Federn positioniert wird, um den Strömungspfad zwischen dem Eingangsanschluss und dem Ausgangsanschluss zu erzeugen, und wobei das Modusventil (30) derart konfiguriert ist, dass, wenn der an dem Eingangsanschluss aufgebrachte Versorgungsdruck den vorbestimmten Schwellenwertdruck überschreitet, der Schieberkörper gegen die Kraft der Federn bewegt wird, um den Strömungspfad von dem Eingangsanschluss zu dem mit der Getriebemotoranordnung verbundenen Ausgangsanschluss (42) des zweiten Modus zu erzeugen.
  2. Anordnung nach Anspruch 1, wobei die Getriebemotoranordnung einen Getriebemotor (50) und eine Zahnradpumpe (52) umfasst, die über eine Drehmomentwelle (51) verbunden sind, wobei der Getriebemotor und die Zahnradpumpe derart angeordnet sind, dass in dem zweiten Modus der Versorgungsdruck durch das Modusventil (30) zu dem Getriebemotor strömt, um zu bewirken, dass sich der Motor dreht, und wobei das Drehmoment aus der Drehung des Motors auf die Zahnradpumpe übertragen wird, um erhöhten Druck bereitzustellen, der zu dem Modusventil zurückgeführt und dem Aktuator bereitgestellt wird.
  3. Anordnung nach Anspruch 1, wobei das Ventil angeordnet ist, um als Reaktion darauf, dass der Versorgungsdruck den vorbestimmten Schwellenwertdruck von 17236,9 kPa (2500 psi) überschreitet, von dem ersten Modus in den zweiten Modus zu wechseln.
  4. Aktuatoranordnung, die ein elektrohydraulisches Servoventil (EHSV), um den Versorgungsdruck bereitzustellen, und einen Aktuator, um den Steuerdruck zu empfangen, und eine Aktuatorüberdruckanordnung nach Anspruch 1 umfasst, die zwischen dem EHSV und dem Aktuator liegt.
  5. Anordnung nach Anspruch 4, die ferner ein Modusventil (20) des elektrohydraulischen Servoventils umfasst, das zwischen dem EHSV und dem Modusventil (30) angeordnet ist.
  6. Anordnung nach Anspruch 4 oder 5, die angeordnet ist, um mit einem beweglichen Teil eines Luftfahrzeugs verbunden zu werden.
EP20306656.8A 2020-12-22 2020-12-22 Aktuatorüberdruckanordnung Active EP4019397B1 (de)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP20306656.8A EP4019397B1 (de) 2020-12-22 2020-12-22 Aktuatorüberdruckanordnung
CA3140331A CA3140331A1 (en) 2020-12-22 2021-11-23 Actuator overpressurising assembly
US17/541,410 US11821443B2 (en) 2020-12-22 2021-12-03 Actuator overpressurising assembly
BR102021025631-1A BR102021025631A2 (pt) 2020-12-22 2021-12-17 Conjunto de intensificação de pressão de atuador, e, método para intensificar uma pressão de abastecimento

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP20306656.8A EP4019397B1 (de) 2020-12-22 2020-12-22 Aktuatorüberdruckanordnung

Publications (2)

Publication Number Publication Date
EP4019397A1 EP4019397A1 (de) 2022-06-29
EP4019397B1 true EP4019397B1 (de) 2024-02-28

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EP20306656.8A Active EP4019397B1 (de) 2020-12-22 2020-12-22 Aktuatorüberdruckanordnung

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Country Link
US (1) US11821443B2 (de)
EP (1) EP4019397B1 (de)
BR (1) BR102021025631A2 (de)
CA (1) CA3140331A1 (de)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4019397B1 (de) * 2020-12-22 2024-02-28 Goodrich Actuation Systems SAS Aktuatorüberdruckanordnung

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US10798866B2 (en) * 2018-08-10 2020-10-13 Cnh Industrial America Llc Depth control system for raising and lowering a work unit of an implement
EP4019397B1 (de) * 2020-12-22 2024-02-28 Goodrich Actuation Systems SAS Aktuatorüberdruckanordnung

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CA3140331A1 (en) 2022-06-22
EP4019397A1 (de) 2022-06-29
US20220194559A1 (en) 2022-06-23
US11821443B2 (en) 2023-11-21

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